Adjustment mechanism



Feb. 15, 1966 H. F. vow THUENGEN 3,234,316

ADJUSTMENT MECHANISM 5 Sheets-Sheet 1 Filed Nov. 15, 1962 Fly. lb

Feb. 15, 1966 H. F. vow THUE'NGEN 3,234,316

ADJUSTMENT MECHANISM Filed Nov. 13. 1962 Sheets-$heet 2 1 H. F- VON THUENGEN 3,

ADJUSTMENT MECHANI SM Feb. 15, 1966 H. F. VON THUENGEN 3,234,

' mwusrmmw MISCHM-H'SM Filed Nov, L5, 1962 5 Sheets-Sheet 4 Feb. 15, 1966 I H. F. VON THUENGEN ,234,

ADJUSTMENT MECHANISM Filed Nov. L5 1962 5 Sheets-Sheet 5 $33 ADJUSTMENT MECHANISM Hubert Freil err von Thuengen, F'riedf ichshafen, Germany, fassignor to Zahnradfabrik Friedrichsha fen, Akti nse slls r t, Eri d uhsh t n, G r y Filed Nov. 13,19 2, so. No. 23 ,794 Claims priority, appliczgiogn Germany, Nov. 25, 1 961,

1' Claims; "to. new

This invention relates to adiustnient'devices, and more paiticularly, to an adjustnl i i device wherein it is desired to translate a shaft radially in a straight line from a central position. The invention also pertains to moving an element having a bore therethr'ongh so that the axis of the bore may be adjusted along a radial line from a central position.

. changing the port position, by moving the axis of the impeller sliaft ona radial line to effect capacity changes;

The objects of the invention are, therefore, to provide translational adjustment control means effecting straight line motion in a simple, compact and certain manner and applicable to any device or machine where adjustment is required of a shaft or a bore.

Another object of the invention is to provide an adjustment mechanism wherein a largedegree of adjustment is afforded in a compact arrangement. Other objects and features of the invention will be apparent from the description that follows.

Briefly, the invention comprises a combination of two eccentrics mounted one within the other, or mounted one on the other, wherein such eccentrics are geared or linked to each other for simultaneous motion. The two eccentric elements have the same degree of eccentricity and are mounted for rotary movement and by virtue of the geared interdependence, or otherwise linked interdependence, manually eflectcd rotation of one eccentric produces (twice the angular degree of rotation of the other eccentric.

The invention is based on the properties of Cardan circles as utilized in straight-line motion mechanisms, e.g., in an epicyclic gear and crank combination.

A Cardan circle combination consists geometrically of a circle of certain diameter anda circle of half that diameter inside and contiguous with the first circle. If the inrer circle being rotated so that its periphery remains contiguous with theoutor circle, any given point on the imicr circle will move in a straight-line which is a diametcr of the outer circle. Also, the center of the inner circle will move on a circle of diameter equal to the diameter of that inner circle. The relativc movement of Cardan circles produces the effect of a 2:1 gear ratio, and such circles can be in the form of inner and outer, i.e., internally toothed, or annular gear for use in various mechanisms.

However, a .Cardan circle arrangement can also be achieved with externally toothed gears, as in the present invention.

A detailed description of the invention now follows, in conjunction with the appended drawing, in which:

FIG. 1a shows geometrically a plan View of the com.- ponents of the invention in centralized non-adjusted position;

United States Patent 0 T. ice

3,234,816 Patented Feb. 15, 1966 ,FlCi. l b illustratcs an adjusted position of the device of FIG. la;

FIG, 10 shows a physical arrangement of the elements in cross sectional elevation; l

FIG. 2 is a longitudinal cross section of a pump embodying the invention;

FIG.-..3 .is a section through I-I of FIG. 2;

FIG. 3a is a section through Su -3a of FIG. 2;

FIG. 4a through 4d shows a modification;

FIG. 5a through 5:] illustrates another modification;

FIG. 6 illustrates a still further modification, and

"1G. 61: shows a modification of FIG. 6.

Referring now to FIG. la there is shown an eccentric element 1 in which is carried another eccentric element 9. The center of eccentric 1 is the point M about which such eccentric is rotativc. The center of the eccentric 9 is the point M Both of these centers are within an eccentric bore 8 having the point M at its center. The eccentricities c and e are equal to each other wherein eccentricity a is the distance from M, to M and eccentricity e is the distance from M to M In the central, or non-adjusted position, shown in FIG. 1, M coincides with M The eccentric l is provided with arcuately arrange gear teeth 2 moshing with an adjusting pinionS, which pinion will be understood to be rotative in either direction to a predetermined extent and on a fixed axis. The eccentric 1 carries a pair of double pinions 5 and 6 which are integral, the smaller pinion 5 engaging fixed arcuate gear 4, which may be attached to housing (not shown). The larger pinion ,6 engages an arcuate gearing 7 on the rim of eccentric 9.

In operation, if pinion 3 be rotated in order to effect adjustment, the eccentric 1 .will be rotated in the direction of the arrow 11 which will cause the pinion combination 5- 6 to roll around the gear 4 via engagement with pinion ,5, causing rotation of pinion 6 in the direction of the arrow shown. Thus, via engagement of pinion 5 with gear segment 4, a rotation of eccentric 9 in the direction of the arrow shown is effected. Such rotation is in the same direction as the initial manual rotation of pinion 3. Assuming that rotation of eccentric 1 takes place to the extent of the angle a the center M of eccentric 9 will move on a circular arc having radius 2 around the point M the center point of eccentric 1, until it reaches the adjusted position M Further, due to rotation of eccentric 9 as effected by pinion 6 acting on gear segment 7, which rotation is opposite to that of the direction of arrow 11, such rotation will take place to an extent of the angle 20:. Accordingly, the center M of the bore 8 will move to thc position M Such movement of the point M occurs on a radial straight line 10 which is nor mail to the initial line joining the directions of cccenlrici ties c and v and the adjusted position of the center point at M as determined by the sum of the equal eccentricitics 1' and 0- The gear ratio between gears 5 and .6 may be varied as may the eccentricities e and e if desired, for efiecting different paths of the point M but in. the present disclosure this is not desired, since to achieve straight line movement of M which is the center of a bore or shaft .to be adjusti d, it is necessary that c =e and also that the total ratio of gears be 1:2, in order to achieve a Cardan circles effect.

Referring to FIG. 10 the elements are shown in physical relationship wherein the disc 1, the eccentric 9 and the gear segment 7 will be seen as supported for rotative bearing on a shaft 1a which in turn may be fixedly supported in a wall 1b. Disc 1 may carry a shaft 10 on which is rotatively supported the integral pinions 5 and 6 that may be connected by an integral collar or sleeve 50.

The gear segment 4 maybe fixed to ground in any suitable manner. The disc 9 is supported by an integral collar 90 rotative within a relatively fixed integral collar 9c.

,1\ practical application of the invention is shown in FIGS. 2, 3 and 311 wherein a pump housing 21 is illustrated, into which extends a drive shaft 22, which drives pump vanes 23 via rotor 23a and is mounted in spaced eccentric discs such as 35, in turn mounted in eccentric discs such as 26, wherein the discs 26 have hearing support within respective walls 34 of the housing. An adjusting shaft 24 is carried on the housing, to which shaft are keyed'pinions such as 25 meshing with gear segments of respective eccentric discs 26. The eccentric discs 26 carry double pinion arrangements 28 and 29 wherein pinion 29 meshes with the teeth on the rim of eccentric 35 and the pinion 28 meshes with a circle of fixed teeth 30 which are integral with the housing. The pinions are integral with each other and each pair is carried on a pin such as 27.

The axial line 31 is the rotative center of the eccentric 26; the axial line 32 is the rotative center of the eccentric 35, and the axial line 33 isthe center of bore 36 in which shaft 22 has bearing support and is therefore the center of shaft 22. e; and e are shown wherein eccentricity e is the eccentricity between the eccentric 26 and 35, and c is the eccentricity between shaft 22 and eccentric 35.

The total overall ratio of the gears 30, 28, 29, at each of shaft 22 is 1:2.

In order to change pump capacity, shaft 22 is moved radially upward or downward by rotation of shaft 24, the functioning of the components occurring as explained in connection with FIG. 1a and FIG. 1b. Thus, shaft 22, as shown in FIGS. 2, 3 and 3a, is in maximum adjusted position.

Reference is now made to FIGS. 4a through 4d wherein FIGS. 4a-c represent a geometric relationship and wherein FIG. 4d illustrates a cross section of the physical arrangement. The adjusting mechanism is shown in cen tral non-adjusted position in FIG. 4a. In the arrangement illustrated, an eccentric or crank disc 41 is rotative about axis M in arcuate slot or channel bearing 49 and is provided with a gear segment 42 with which a reciprocal gear rack 43 meshes which is pushed or pulled to effect the degree of adjustment required for radial movement of bore 47 in a second eccentric 46 having eccentricity 2 between axis M and axis M and being rotative on axis M Eccentric 46 is rotatively supported in an aperture in eccentric 46 and may receive lateral restraint by guide blocks 40.

Gear 44 also having M; as its axis and having a radius equal to the eccentricity e carried on an arm 43 integral with eccentric 46. Gear 44 meshes with a fixed internal gear segment 45 which is concentric with point M and the radius of gear 45 is twice that of gear 44. The axis M of bore 47 which axis is to be radially and linearly has eccentricity e with respect to axis M which coincides in the non-adjusted position of FIG. 4a with axis M and passes through the pitch circle of gear 44.

If now rack 43 be pushed to the right, as seen in FIG. 4b, eccentric 41 is rotated through angle a and gear 44 rolls within gear segment 45 to etfect rotation of eccentric 46 about axis M The axis M is thus rotated on a circular are around axis M into the position shown in FIG. 4b, while the axis M rotates around axis M to the extent of the angle 20:. The eccentricities e and e; are equal and the gearing arrangement effects motion of eccentric 46 in an opposite rotative sense with respect to the rotational direction of eccentric 41. In accordance with the principles of a pair of Cardan-circles, the gears 44 and 45 having the ratio 1:2, the axis M of the shaft 47 carried by eccentric 46 moves in a straight line on a diameter of gear 45. The final position of point M is shown in FIG. 40, such maximum adjusted travel of the point being equal to the sum of the eccentricities e and e FIGS. 5a through 5d represent a further embodiment fit Referring to FIG. 3, the equal eccentricities 5 for an adjusting mechanism comprising a Cardan circle combination. In opposition to the modification shown in FIGS. 4a through 4:? the eccentrics are arranged one upon the other instead of one within the other. The eccentric 56 being rotatable about axis M comprises a gear segment 52 which meshes with a tooth rack 53. As represented in FIG. 5:! the eccentric 56 is supported on a pin 58 extending into the bore 51 and being secured to a fixed wall 59. A further eccentric 57 is rotatably mounted on eccentric 56. The eccentric 57 carries a pinion 54 which is rotative about axis M; of eccentric 56.

When the eccentric 56 is rotated through rack 53, pinion 54 rotates within the internal gear 55 concentric with M As the radii of the gears 54 and 55 have the ratio 1:2 and the eccentricities 0 and 0 are equal, the axis M of the adjustable eccentric 57 is translated radially in a straight line from its central position M Referring now to FIG. 6, the Cardan-circles arrangement therein shows how certain applications where the radii of a pair of Cardan-circles is so small that the actual use of Cardan-circle gearing is impractical, a relatively large gearing can be utilized by being positioned outside the eccentric portion of the device. Thus, the eccentric discs 61 and 68 are provided wherein disc 61 may be rotated on axis M via the gear rim 62 in conjunction with the manually rotative adjusting gear 63. The eccentric disc 68 is rotative on axis M and mounted rotatively within a bore in disc 61 being connected by a link 69 to the rollable element 64, which will be understood to have a frictional gripping surface engaging the arcuate coacting component 65. Link 69 may be pivoted by pins 64a and b to eccentric 68 and element 64.

The elements 64 and 65 can be gear-toothed, as indicated in FIG. 6a for positive engagement, and element 64 will be noted as being pivotaly carried at 640 on eccentric disc 61.

A bore 67 in the eccentric disc 68 is provided and it will be understood that the axis of the bore M is to be radially adjusted in a straight line. Thus, eccentric disc 61 being rotative around the axis M and eccentric disc 68 being rotative around axis M in keeping with previously described modifications, the rotation of axis M to the extent of angle a about axis M, produces double rotation of the axis M to the extent of angle 20: about axis M The Cardan-circles relationship is retained by making the radius of the rolling component 64 half of the radius of the fixed arcuate element 65, or as in FIG. 6a, the pitch circles of the gearing are in the ratio of 1:2.

The link 69 and gear 64 can be duplicated on the other side of the eccentrics, using the same pins 64a, b and c and thus such links effect a guide to maintain eccentric 68 within eccentric 61.

In retrospective, it will be apparent that all forms of the invention carry out the principle of Cardan-circles in that, in effect, although the structure may be quite dissimilar from the basic Cardan-circle structure, the mechanical action remains the same in that in essence a wheel is revolved inside another wheel of twice the diameter so that for each degree of rotation of the smaller wheel with respect to the inner periphery of the bigger wheel, the smaller wheel rotates two degrees about its own axis. In effect, the eccentricities c and 2 as described herein, are the length of crank throws which correspond to the radius of the smaller wheel, where such crank throws are actual physical parts in such structures wherein one eccentric disc is not actually carried within an aperture of the other eccentric disc. In instances where the eccentric disc is actually carried within an aperture of the other eccentric disc, then the eccentricities correspond additively to the radius of the larger wheel, while each eccentricity remains equal to the radius of the smaller wheel. Since the eccentricities are the measure of the spacing between the various axes, it will be apparent that the axis of the element to be adjusted must pass through the pitch circle of the smaller wheel, if the smaller wheel be a gear, and thus such axis can be considered a point on the periphery of such smaller wheel which travels on a diameter of the larger wheel.

Having thus described this invention, I am aware that various changes may be made without departing from the spirit thereof, and therefore am not limited to the precise illustrations herein given, except as set forth in the appended claims.

Iclaim:

1. An adjusting mechanism for a member comprising one rotative element, and manually adjustable means whereby said element is manually rotatively adjustable to selected positions; and another rotative element to be radially adjusted with respect to its axis of rotation in response to rotative adjustment of said one element, said elements being mounted in eccentric contiguity with each other, control means whereby the rotative movement of said adjustable one element effects rotative and radial movement of the other element, said control means comprising a fixed element, and further comprising actuating means connecting said elements with said fixed element wherein rotative adjustment of said one element effects rotation of the other element by virtue of said actuating means and said radial movement then occurring by reason of the eccentric eontiguity of said elements, and said member being operatively connected to said other element for radial adjustment.

2. A straight line adjustment mechanism for a rotary pump comprising a pair of rotative elements mounted for rotation on parallel spaced axes, means connecting said elements wherein manual rotating of one element effects rotation of the other element with respect to the axis of said one element and simultaneous additional rotation of said other element about its own axis whereby said other element is adjusted radially, and means whereby the total degree of rotation of said other element is twice that of said one element, and means whereby said other element effects support of a rotary pump shaft to adjust the capacity of said pump, said means comprising a bore in said other element and the rotary pump shaft extending into said bore, said shaft and bore having a common axis.

3. A straight line adjustment mechanism comprising a housing having at opposite ends thereof an axially aligned duplication of a first gear rotative about an axis and having a circular aperture having an axis spaced from said first axis, a second gear carried rotatively in said aperture and being rotative about the axis of said aperture, said second gear having an axis coinciding with the axis of said first gear when said gears are in an initial position with respect to each other, means for effecting an adjusting rotation to a selected angular degree of said first gear, a fixed gear, a pair of integrally connected pinions rotatively carried by said first gear, one of said pinions meshing with said fixed gear and the other of said pinions meshing with said second gear, the overall gearing ratio being 2:1 whereby angular adjustment of said first gear effects double the angular rotation of said second gear, and whereby the axis of the aperture therein is translated radially with respect to the axis of said first gear upon angular adjustment thereof.

4. A straight line adjustment mechanism as set forth in claim 3, each of said second gears having a bore and a rotary shaftextending between said bores wherein said shaft is radially adjusted by adjustment of said first gears.

5. A straight line adjustment mechanism as set forth in claim 3, including a means extending between said first gears for effecting manual rotative adjustment thereof in unison.

6. A straight line adjustment mechanism as set forth in claim 3, each of said second gears having a bore and a rotary shaft extending between said bores wherein said shaft is radially adjusted by adjustment of said first gears, including a means extending between said first gears for effecting manual rotative adjustment thereof in unison.

'7. In a device as set forth in claim 1, said actuating means comprising a gear device carried by said one element and being rotative upon adjustment of said one element, to effect rotation of said other element.

8. In an adjusting mechanism as set forth tin claim 1, said actuating means comprising a gear device carried by said one element and being rotative upon adjustment of said one element to effect rotation of said other element, said gear device comprising a pair of coaxial gears, said other element having gear teeth meshing with one of said coaxial gears and said fixed element being a gear coacting with the other of said coaxial gears.

9. In an adjusting mechanism as set forth in claim 1, said actuating means comprising a gear device carried by one of said movable elements and being rotative upon adjustmentof said one element to effect adjustment of said other movable element, said movable elements having spaced axes and being rotative thereabout, and said fixed element comprising a gear segment.

10. A straight line adjustment mechanism for a rotary pump comprising a pair of rotative elements mounted for rotation on parallel spaced axes, means connecting said elements wherein manual rotation of one element effects rotation of the other element with respect to the axis of said one element and simultaneous additional rotation of said other element about its own axis and means whereby said other element is adjusted radially and the total degree of rotation of said other element is twice that of said one element, and means whereby said other element effects supports of a rotary uump shaft to adjust the capacity of said pump.

11. A mechanism as set forth in claim 10, wherein the means connecting said elements comprises the support of one element by the other element to effect the first mentioned rotation, and means connected to the othe'r element for effecting said simultaneous additional rotation responsive to rotation of said one element.

12. A straight line adjustment mechanism comprising i 13. A mechanism as set forth in claim 12, .includinga shaft passing eccentrically into said second disc, and pump rotor means carried by said shaft for effecting straight line radial displacement thereof upon adjustment of said first disc. I t

14. A straight line adjustment mechanism comprising a manually rotative first elemcnt and means for effecting angular adjusting rotation thereof about an axis, asec ond rotative element carried by said first element and having its axis of rotation eccentrically displaced with respect to the axis of said first element, and means whereby said first element can be rotated about its axis during an adjusting rotation while said second element rotates about its axis during said adjusting rotation to twice the degree of rotation of said first element, said second element coittaining an axis to be adjusted which moves during adjustment of said first element in a straight radial line with respect to the axis of said first element and remaining parallel thereto, and said axis to be adjusted coinciding with the axis of said second element when said elements are in an initial position. i

15. A straight line adjusting mechanism comprising a first element manually rotative about an axis, and means for effecting rotational adjustment of said first element about said axis, a second element carried by said first element and rotative about an axis parallel to and spaced from said first mentioned axis, and rotative about said first mentioned axis when said first element is rotated,.a fixed gear element and a gear carried. by said second element engaging said fixed gear element with a 2:1 ratio effective to produce twice the angular rotation of said second element by drive between said gear and said fixed gear element when said first element is afforded an adjusting rotation, said second element containing an axis to be adjusted parallel to the above mentioned axes and spaced initially from said axis of said second element by an amount equal to the initial spacing of the axes between said first element and said second element when said elements are in an initial position and coinciding with the axis of said first element in said initial position and moving in a straight radial line with respect to and parallel to said'other axes during the course of adjustment.

16. A straight line adjustment mechanism comprising a pair of rotative elements mounted for rotation on parallel spaced axes, means connecting said elements wherein rotation of one element effects rotation of the other element with respect to the axis of said one element and simultaneous additional rotation of said other element about its own axis whereby the total degree of rotation of said other element is twice that of said one element wherein the means connecting said elements comprises a link pivoted to one of said elements and a gear pivoted to the other of said elements, said link being pivotally connected to said gear and a fixed gear component engageable by said gear wherein the ratio of said gear to said fixed gear component is 2:1.

17. A straight line adjustment mechanism comprising a first gear rotative about an axis and having a circular said first gear, one of said pinions meshing with said fixed Y gear and the other of said pinions meshing with said second gear, the overall gearing ratio being 2:1 whereby angular adjustment of said first gear effects double the angular rotation of said second gear, and whereby'the axis of the aperture therein is translated radially with respect to the axis of said first gear upon angular adjustment thereof.

References Cited by the Examiner UNITED STATES PATENTS 1,432,494 10/ 1922 Regen 74435 1,438,495 12/1922 Johnson 74-52 1,557,223 10/1925 Warner 74-52 1,602,740 10/1926 Belcher l03--120 2,506,736 5/ 1950 Oschwald 7452 2,898,862 4/1959 Brundage 103-120 BROUGHTON G. DURHAM, Primary Examiner. 

1. AN ADJUSTING MECHANISM FOR A MEMBER COMPRISING ONE ROTATIVE ELEMENT, AND MANUALLY ADJUSTABLE MEANS WHEREBY SAID ELEMENT IS MANUALLY ROTATIVELY ADJUSTABLE TO SELECTED POSITIONS; AND ANOTHER ROTATIVE ELEMENT TO BE RADIALLY ADJUSTED WITH RESPECT TO ITS AXIS OF ROTATION IN RESPONSE TO ROTATIVE ADJUSTMENT OF SAID ONE ELEMENT, SAID ELEMENTS BEING MOUNTED IN ECCENTRIC CONTIGUITY WITH EACH OTHER, CONTROL MEANS WHEREBY THE ROTATIVE MOVEMENT OF SAID ADJUSTABLE ONE ELEMENT EFECTS ROTATIVE AND RADIAL MOVEMENT OF THE OTHER ELEMENT, SAID CONTROL MEANS COMPRISING A FIXED ELEMENT, AND FURTHER COMPRISING ACTUATING MEANS CONNECTING SAID ELEMENTS WITH SAID FIXED ELEMENT WHEREIN ROTATIVE ADJUSTMENT OF SAID ONE ELEMENT EFFECTS ROTATION OF THE OTHER ELEMENT BY VIRTUE OF SAID ACTUATING MEANS AND SAID RADIAL MOVEMENT THEN OCCURRING BY REASON OF THE ECCENTRIC CONTIGUITY OF SAID ELEMENTS, AND SAID MEMBER BEING OPERATIVELY CONNECTED TO SAID OTHER ELEMENT FOR RADIAL ADJUSTMENT. 